Clutch



" Sept. 24,1946. c. M. EASQN CLUTCH 'Filed Jan. 22, 1945 5 Sheets-Sheet 1 INVENTOR.

Clarerwefii [626072 s t. 24, 1946. c. M, EASON 2,408,301

' CLUTCH Filed Jan. 22, 1945 5 Sheets-Sheet 2 Sept. 24, 194

C. M. EASON CLUTCH Filed Jah. 22, 1943 5 Sheets-Sheet 4 v IINVENTOA/ Lia/ 7206171015072,

Sept. 24, 1946.

.c. M. EAS ON CLUTCH Filed Jan. 22, 1945 5 Sheets-Sheet 5 Patented Sept. 24, 1946 UNITED STATES' PATENT OFFICE CLUTCH V I Clarence M. Eason, Waukesha, Wis. Application January 22, 1943, Serial No. 473,208

a the act of applying the brake the clutch is released, and in releasing the brake the clutch is applied, assuring proper control of the operating parts at all times. More specifically, I provide an axially shiftable non-rotatable brake member and associated means whereby'axial shifting of the brake member in one direction into nonbraking or releasing position effects the clutch engagement, and axial shifting of the brake member in the opposite direction into its operative r braking'position effects the declutching operation, the latter operation being assisted by energy stored in the brake servo means by overrunning of the shaft controlled by the clutch incident to the declutching operation.- The clutch is also preferably provided with self-energizing means which functions after initiation of the clutching operation to hold the friction clutch members, preferably cone members, in clutching contact under considerable pressure.

Another important aspect of the present invention is the use of the servo action for the interrupted rotating brake member, in order that the initial force applied to the non-rotating brake member may be held to very low values, such as may be readily controlled by means of a conventional foot treadle without causing undue fatigue of the operator. 7

Another important feature of my invention is that the clutching and declutching operation, ac-

companied by the concomitant relative movement of the braking member, out of and into cooperating braking contact, is effected by axial shifting of a non-rotatable brake member and in such manner that rotation of the clutch controlled'shaft is not necessary for effecting the clutching. and declutching operation. My improved clutch gives complete control of the driv- 33 Claims. (01.192-36) Further objects and advantages of my invention will. appear from the detailed description. Inthe drawings:

Figure 1 is a fragmentary side view of apress, with clutch means embodying my invention applied thereto; I

Figure 2 is a front view of the press and the clutch meansshown in Figure 1; l

Figure 3, is a view, on an enlarged scale, of the clutch means. and associated parts, shown in front elevationat the lower half of this View and in axial section at the upper half of this view,

certain parts in the upper half being shown in elevation and certain parts being broken away;

Figure 4 is a fragmentary axial sectional view of the'clutch means, partly broken away and in section to show the cam rings and balls andassociated parts, on an enlarged scale;

en shaft. throughout the entire 360 degrees of I plied to a flywheel or analogous member of a press or like machine without necessitatingobjectionable changes in the flywheel and associated parts,v articularly the bearings therefor.

Figure? is a sectional view taken substantially on line 1-1 of Figure 4;

Figure 8 is a diagrammatic view illustrating the relation between the clutch and the brake members, and the effect of the overrunning of the clutch controlled shaft and associated parts;

Figure 9 is a vertical transverse sectional view of the bracket supporting the clutch operating shaft, showing the over-center spring and pawl means of the clutch control mechanism; and

Figure 10 is a sectional view taken substantially on line I0l0 of Figure 9, certain parts being shown in elevation and certain other parts being broken away.

I have illustrated the clutch mechanism of my invention as applied to a press of known type, by way of example, to which it is well suited, though it is to be understood that my clutch mechanism is in no way limited to that particular use, since it is suitable for many other purposes, and may be applied to any use to which it is suited. The press shown is a so-called back geared type where the clutch is located ona secondary or back shaft which, because of the ear reduction, makes several revolutions to one revolution of the main crank shaft. The clutch structure, however, can very readily be applied directly to the crank shaft and controlled by substantially the same type of mechanism which is used to control my improved clutch when mounted on a back shaft.

In Figures 1 and 2 of the drawings I have shown fragmentarily a portion of a frame 7 of a press P of known type, thi frame having mounted therein, in a suitable manner, a rotatable crank shaft l I. A bracket I2 is bolted or otherwise suitably secured to frame f at each side thereof and extends upward and rearward therefrom. Each of the brackets l2 supports a bearing structure 53, and these bearing structures rotatably support a back geared or secondary shaft M extending transversely of frame 9 below and in back of the crank shaft M. It will be understood that the press is provided with a ram connected by a connecting rod to the crank of shaft l l, and associated parts, which have been omitted, for clearness of illustration and as not being necessary to a clear disclosure of my invention. A spurpinion I i keyed on one end of drive shaft Id, at the opposite side of frame I to that shown in Figure 1, and meshes with a gear is secured onthecrank shaft H at the same side of the frame, whereby rotation of shaft J4 imparts rotation to the crank shaft.

Shaft Hi extends outwardly beyond'thebearing structure 13 at the otherside of frame f, thatis, at the side thereof remote from pinion l5 and gear l8, and this portion of shaft 1.4 is tapered outward'at i8 for a portion of its length, being provided at its outerend with a reduced threaded end 19. A comparatively heavy mounting collar is rotatably supported on shaft l4, adjacent the side of frame .7" remote [from pinion I15, by means of ball bearings 2110f knowntype, each having an inner race in the form of a relatively long sleeve 22 fitting about shaft M, the sleeves being disposed in endwise contact. A flanged ring 2.3,is secured to shaft M, by one or more do point set screws, one of which is shown at 2 with its flange engaging the rabbeted inner end of the inner sleeve 22 in endwise contact therewith. Collar 29 is provided, at its outer end, with an inwardly extending flange25 extending about the outer end portion of the outer sleeve 22 and in contact with the outer race of. the outer bearing- 2!, and is further provided, at "its inner end, with an outwardly extending circumferential .flange 26. The outer race of the outer bearing 12.! contacts the inner face of flange 25 and restrains collar 28 against endwi-se movement inward along shaft 14, the outer bearing 2| thus functioning as a thrust bearing. Flange 26 is provided with a plurality of openings bored therein, one of which is shown at 2'5, these openings preferably being disposed close together. Two of these openings, preferably two diametrically opposite openings, receive reduced studs 28 at the inner ends of hollow plungers 29 *slidably mounted in corresponding bores in the hub 3-3 of a flywheel 31 of suitable construction. Each of the plungers 29 is urged inward by a coil com-- pression spring 32 extending thereinto and seating therein at its inner end, the outer end of spring 32 seating against a retaining ring 33 fitting in a corresponding annular groove in the outer end of hub and bolted thereto. Ring 33 screws onto the threaded outer end portion 3-4 of collar 20. It will be seen that by rotating collar '28 relative to flywheel 3!, the latter may be adjusted axially in either direction. For that purpose I preferably provide a spanner wrench having two studs equal in thickness to flange 2t and disposed to enter the two diametrically opp-osite openings 21 which receive the studs 23 of the plungers 29. By means of the stud of the spanner wrench, the stud 28 of the plunger may be displaced outwardly so as to release flange 26 from hub 30, after which the collar 20 may be turned by means of the spanner wrench a distance equal to that between two adjacent openings. By repeating that operation the flywheel 3| may be adjusted to the desired extent in either direction axially, for a purpose which will be explained more fully hereinafer. An oil seal member 36, of known type, is disposed within the inner end portion of collar 2! confined therein between the outer race of the inner bearing 21, the retaining ring 23, and a snap ring 31 engaging in a corresponding groove in the inner face of collar 29.

A tubular hub Ml, having a tapered bore corresponding to the tapered portion l8 of shaft it. is secured tightly on portion l8 of shaft I 4 by a nut M screwing onto stud l9 and an associated lock washer 42 held in pressure contact with the outer end of hub 48 by nut 4!. Hub 40 is further secured against rotation relative to shaft M by a key 43 engaging in keyways in hub is and in portion I8 of shaft M, the lock washer 42 having a portion struck therefrom and engagin in the keyway of hub 48 at the outer end thereof. It will be seen that hub 46 is effectively secured to shaft M in a .manner to prevent relative movement between these two members, and the inner end portion of this hub is interiorly recessed to accommodate the outer end portion of the sleeve 22 of the outer bearing 2!. Hub 49 is also provided, at its inner end, with an exterior circumferential flange 45 having, at its outer circumference, a flange 45 extending outward lengthwise of hub 48. A loose thrust washer Q8 preferably of nonmetallic anti-friction material is interposed between the flanged end 25 of the flywheel adjusting sleeve 29 and the inner face of clutch hub 463. When the flywheel is rotating freely on its ball bearing-5 2!, with the shaft and clutch stationary, there is a slight running clearance between these thrust surfaces, but when the clutch is engaged and there is no relative rotation between flywheel and clutch, the axial thrust reaction due to the servo strut action (to be later described) is transmitted directly from the clutch hub to the "flywheel itself through this thrust washer. At no time is there any axial thrust on the ball bearings 2|, due to clutch servo strut action. These bearings do'not take end thrustexcept the very small amount which might be required to maintain the flywheel and the driving clutch cone in proper axial alignment. In this regard, it will be noted that the thrust ring 48, in its abutment against the outer end of collar '25], cooperates with the outer bearing 2| for restraining the mounting collar 243 and flywheel 3| against endwise movement in either direction.

A female clutch member 52, having an outwardly converging clutch surface, is suitably secured, conveniently by bolting, to flywheel .31 at the outer side thereof. Clutch member 52 cooperates with a male clutch member '53 having riveted thereto a clutch lining 54, the latter clutch member being bolted to a flanged ring 55 mounted about hub 40, the exterior surface of which is of stepped formation, as shown. A flanged collar 56 is secured to ring '55 by bolts, one of which is shown at 57 which secure collar til and clutch member 58 together, the bolts 57 screwing into the heavy flange at the outer end of collar 56, and clutch member 53 being rabbeted for reception of the flange of ring 55, the collar and the clutch member being thus effectively secured together with the flange of ring 55 clamped between the inner portion of clutch member 53 and the flange at the outer .end of aswill be explained more fully later.

collar 56,- bolts 9 51 positively securing the parts together; W

-Ring:55 and flange 45 of hub are connected by 1. clutch: self-energizing mechanism comprising rigid struts 60 of dumbbell formation, constituting drive transmission members, and lengthwise compressiblespring struts'6l constituting energy storing members. The struts 60 are inclined transversely of the axis of shaft 14 in such direction that they act under compression to transmit sitely to struts 69 and function both as energy storing members and as reverse drive'members,

In practice' I usually provide three struts 60 and three struts 6|, though a larger number of struts may be used if desired; Preferably, the struts are constructed and connected tothe partsass'o'ciated therewith in the manner shown and described in detail'in my copending applications, Serial No.

279,899, filed June -19, 1939, and Serial No.

-tion of hub 40 outward beyond ring 55, in endwise abutting relation thereto with an intervening thrust ring 64. Ring 63 i provided with an outwardly extending circumferential flange secured, asby means of bolts, one of which is shown at 65, to hub 65 of a malebrake member Ei'l' having an outwardly converging braking surface. provided b a brakelining 68 riveted or otherwise suitably secured to the rim of member 61. A second cam ring 19, provided with an inner circumferential inwardly extending flange H, is screwed on the outer end ofhub 40, at 12, with flange H in abutment with a shoulder 13 of hub 40; Lock washer 42 is maintained in pressure contact with the outer end of ring 10 by nut 4| It will be seen that ring 19 is-thus fixed on hub 49 for rotation therewith, and also provides an abutment member fixed against axial movement will appear more fully later. Lock pins 10a further secure 'ringflllagainst turning on hub 40.

1 As is shown more clearly in Figures 4 and 7,

rin'gjlll is provided, in its inner face, with three equally spacedgrooves or recesses 15 increasing grooves or recesses 16, corresponding to the arranged in cooperating pairs, the rings 63 and lll b eing properly related to that end, and provide camrunways for steel balls l8 mounted therein. It will be seen that turning movement of. ring 10 in the direction in which shaft I4 is driven, occurring while corresponding turning "movement 'of the other cam ring 63 is" being rein either direction, whereas the male clutch :member '53 and the male brake member 57 are disposed in endwise abutting relation and are mounted for axial movement relative to hub 40, as well as for turning movement thereabout, as

jgro'oVes or recesses 15 but disposed reversely theret'o, decreasing in depth in the direction of rotation of'shaft 14 when that shaft is driven lthrough' the clutch means, in a manner to be described? The'recesses or grooves 15 and 16 are 6 tarded' or blocked, will cause the balls .18. to move into the shallower ends of the grooves 15 and 16,-thus forcing cam ring 63 axially inwardly away from ring 10 a distance somewhat less than one-half the diameter of'the respective balls 18, equal to approximately one-third of the diameterof the ball. At that time eachofwthe balls 18 is at the shallow ends of the two cam runways, as will be clear from Figure 4, and, if the.

brake member 61 is held against rotation, to block further rotation of the cam ring 63, this will cause the clutch 52,53 to become declutched and will function to stop rotation of shaft l4.

Brake member'fi'l cooperates with a female brake member 89 of dome shape, provided at its inner end with a rim 8| having an inner braking surface cooperating with the braking surface 68 of member 61. Brake member.80 is provided, at its outer end, with an inwardly extending hub 82 formed with an interiorkeyway 83 slidably receiving a key 84 seating in a corresponding recess in a bushing 85 fitting within hub 82,: An adjusting nut 8l, of cupped shape, is threaded on the outer end portion of bushing \85, this nut being provided at its inner end with an outwardly extending circumferential flange 88 seating against the outer end of hub 82. A flanged retaining ring 89 is secured to the outer end of brake member 89 by means of bolts, one ofwhich isshown at 90, having socketed heads for reception of a suitable socket wrench. Brake member 89 is held against turning movement, but is free for axial shifting movement in either direction, as will be explained more fully later. Normally, flange 88 of nut 81' is clamped tightly between 'hub 82 and ring 89, effectively securing these parts together and restraining member against axial movement relative to bushing 85. By slightly loosening the bolts 90, sufficiently to release'the clamping action of ring 89, nut 81 may be rotated by means of a suitable wrench, for

which purpose nut 81 is provided at its outer end with a hexagonal element 9|, rotation of the nut serving to effect adjustment of brake member 80 axially along bushing in the desired direction and to the desired extent,'after which by-tightening the bolts 99 the parts are clamped together as before. I a

-A flanged cap 93 is bolted to cam ring 10, at the outer side thereof, and extends therefrom outward about and acrossthe outer end of shaft l4. Cap 93 is provided, at its outer end, with a hub 94 disposed coaxially with shaft l4, in which is fixedly secured, by welding or in any other suitable manner, the inner end of a stub shaft 95. A thrust ball bearing 96 is mounted about the inner endportion of stub shaft 95, with its inner race abutting the outer end of hub 94, this bearing 96 being disposed in an annular recess in the inner face of a cam ring 91 shown more clearly in Figures 5 and'6. Ring 91 is provided with an outwardly projecting hub 98 having outer end of stub shaft 95, with an intervening lock Washer I04. The cam ring N19 is similar in construction to thecam ring 91. and is provided with an inwardly extending hub. I05 which'is appropriately slotted to'provide coupling projections disposed :to engage between the projections 89 :of ring 9], whereby the rings 9?! .and I are coupled together for turning movement as a unit. It will be seen that the acam rings 91 and I00 are restrained against axial movement away from each other, by the thrust/hall bearings '96 and I01 and associated parts.

The :bushing .85 is slidably mounted On the cam rings 9.! and III!) for relative axial movement in either direction, .and this :bushing supports the brake member 80 for relative axial movement in either direction, .as above described. A cam shift ring I08 is disposed within bushing 85, between the rings 91 and mo, and is secured to bushing 85 by set screwsIflS. The axial extent or width of ring N38 is less than the axial distance between .the rings '9] and fill), as will be clear from Figure 4. Cam :ring 91 is provided in its outer :face with three equally spaced grooves or depressions III which decrease in depth in the di- :-rection of rotation of shaft I4. The shift cam ring IE8 is provided in'i'ts inner face with three grooves or recesses H2 which are reversed relative to the grooves or recesses III and, accordingly, increase in depth in the direction of rotation of shaft Id. .At its outer face the shift cam ring 1'08 is provided with three grooves or renesses H3 disposed in the same manner as the grooves or recesses I I I, and cam ring It!) is provided in its inner face with three grooves or recesses .I I4 disposed in the same manner as the .grooves or recesses H2 in the inner fac of the shift cam ring We. It will :be understood that the grooves or recesses HI and H2, and the grooves or recesses II3 and IM are disposed in cooperating pairs, each pair of grooves providing a cam'runway for a steel ball I I5 mounted therein. A brake lever I6, provided at its inner end with an annular head III, is suitably secured, conveniently by rivets 'I I8, to the inner end of .cam ring 91.. It will be clear that by moving lever .Il B in one direction and thereby turnin ring 91 in :a direction opposite to the direction of rotation of shaft t4, the shift cam ring IGB will be .forced to the left, as viewed in Figure 4, thus shifting the bushing I35 axially toward the :left:and with it the brake member 811, moving the latter away from brake member 61 into brake releasing position. By turning the brake lever in the opposite direction, and thereby imparting corresponding turning movement to the rings 8.? and Hill, the cam shift ring 168 will lee-forced to the right, into the position shown in *l igure 4, being then spaced from ring I09 a distance somewhat less than one-half the diameter of the respective balls H5. This movement of ring I08 shifts the brake member 83 toward the right, as shown in Figure 3, into engaging and brake setting relation to the brake member El. Preferably, the ball receiving recesses or runways of the rings 97 and Idli and IE8 are disposed substantially tangent to a circle struck from the axis of stub shaft I35 which, as noted, is coaxial with shaft I4, rather than being substantially concentric with the axis of the latter :shaft as are the recesses I5, 15 :of rings -63, -13, since I find that this'tangent arrangement of the grooves or recesses of the rings 97 and Hi0 and I138 is more efiicient for obtaining the desired cammin'g action.

Brake member 80 is provided, at diametrically opposite points thereof, with integral bosses :Iii through which are secured :pins II;8, convenient- 1y by nuts screwing .on their inner ends, these pins being providedat their outer ends with substantially spherical heads =Izl9. Heads I I9 receive socket members I20 fitting thereabout, securcdto the :upper ends of thrust rods I21 in a suitable *manner, conveniently :by nuts -I 22 screwing upon the rods. The lower ends of rods I2 I have socured thereon, conveniently by nuts I23 screwing onto the rods, eye members I24 which receive pivot pins I25 suitably secured, convenient- .lyby nuts I26, to outwardly projecting arms I21 of a torque resisting yoke I28 bolted to a flange I29 at the outer end of a bracket I30 bolted to frame I of the press. The thrust rods III restrain brake member against turning movement, while permitting axial movement of this member -80 either direction, there being slight looseness between the member-s [I9 and I20 of the ball and socket connections, sufiicient to prevent objectionable bindingin the shifting of brake .member #8. A brake operating rod I34 ispivoted at its upper end to the lower end of brake lever IrI B, as shown in Figure l, and extends therefrom to an arm --I3-I pivoted at its lower end, at I32, to the lower end of rod I34. Arm IE4 is secured at its upper end upon the outer end of a shaft I33 rockably mounted through bracket I38. By turning shaft I33 in proper direction the cam ring 91 may be turned in either directiondesired for shifting brake member 8 axially into brake releasing position or brake setting position rela- .tive to brake member 61, in the manner above described. Within the broader aspects of my invention, any other suitable means may be provided [for imparting the desired turning movement to the cam rings 9 I!!!) in either direction.

In Figure 8 I have shown diagrammatically the parts in the positions which they occupy when the braking means has been setand the clutch member 53 has been shifted into declutched positicn. The arrowa indicates the direction of rotation of shaft 14 when it is driven by the flywheel s1 through the clutch. Referring first to the mode of operation which occurs when the clutch structure is revolving, it will be seen that when the brake member 80 is shifted toward the right it engages brake member 5], thereby exerting braking action thereon, which retards or stops further .rotation of thisinterruptable .brakemem- .ber .6 almost immediately. Thereu-pon, the continued rotation of the shaft I4 and the clutch releasing servo .cam ring 10 .acts through the servo balls'JB to shift the other cam ring 63 toward the right. This shifts the driven clutch element 53 towards and into its clutch releasing position, such being effected substantially entirely from servo energy. As the shiftable cam ring 63 and interruptable brake drum .6] shift toward the right in this servo-actuated clutch releasing operation, the controllable brake ring 8!) follows up this shifting movement, .oontinuing to maintain its frictional pressure against the interrupt- ..ab-le brake members]. The shifting of the driven .clutch element 53 into clutch releasing position .compresses-thesprings G-I of the spring distended reverse acting toggle struts ,6I, storing energy in these springs which effective to .reengage the .olu-toh .as soon as the controllable brake .ring '80 is backed away from the .interruptable 'brake drum 6] in the .clutch enga ing operation. The controllable brake .member 80 may be shiftedinto this clutch releasing position solely under manual energy, or it may be actuated hydraulically or pneumatically, .or it may respond to an automatic one-cycle stop mechanism which can be set to -produce single trip operation .or repeating operation of the punch press,as desired. .In the 9.. embodiment illustrated, I have shown the con trollable brake-member 80 responding tosuch a matic mechanism "comprises a biasing spring I48 (Figures 9 and which acts alternatively to shift the controllable brake member 80 either toward the clutch releasing position or toward the clutch engaging position. When said brake member is shifted toward its. clutch releasing position this Ibia'sing spring I48 is operative to exert more pressure tending to movethebrake member in this direction than the toggle springs M can exert in the opposite direction. Hence, when the clutch is released the brake member 80 remains in this clutch releasing position, shifted to the right in opposition to the pressure of the toggle springs'fil'.

In this clutch releasing position of'the parts, a braking force is also exerted on the driven shaft I4 from the. brake members 61, 80. vThis braking force iseffective through the cam ring 63, thrust washer 64, driven clutchelement 53 and toggle struts to the driven shaft. Theservo balls 18 are also operative to transmit braking force through the positive end stops at the'opposite end of the inclined runways 15, I6 and through the cam ring 10 to the driven shaft I4. Thus, braking retardation is continuously maintained on the driven shaft l4 so long as the clutch remains released. It should be noted that inthe above described clutch releasing operati0n,the

trollable brake member 80 is merely backed away from the int'erruptable brake member 61 in a shifting movement toward'theleft. This permits the compression springs 6| on the spring struts 6 I to shift the driven clutch element .53 back into clutch engaging position, whereupon the self-energizing struts 60 complete the'high pressure engagement of the clutch surfaces. The clutch is now engaged and the brake released.

Referring now to the operation of the clutch when the flywheel is not being driven, the operation of releasing the clutch at this time is likewise performed by shifting the controllable brake member 80 to the right. This merely transmits corresponding shifting force to the then inert brake drum '6'! which in turn is transmitted through the cam ring 63 and thrust washer 64 to the driven clutch element 53. Ihus, this driven clutch element is shifted to clutch releasing position solely by shifting force imparted to controllable brake member 80, and without any servo boost. It will be seen that the clutching and declutching operations, accompanied by the brake releasing and the brake setting operations, may

be performed at any -point in .the rotation of shaft I4, and, accordingly, of the crank shaft driven from shaft I4, which is advantageous in that rotation of shaft I4 or of the crank shaft of the press, through a definite angle or througha complete revolution is not necessary in order to effect either the declutching or the clutching operation.

From what has been said it will be seen that the clutch releasing operation, when shaft I4 is being driven, is started by movement of the brake member 80 in brake engaging direction, and is completed by servo energy derived from rotation of shaft I4; and the clutch engaging operation is started by movement of the brake member 80 in brake releasing direction and is completed by the self-energizingtorque transmitted through the toggle struts 60, the brake means being set upon completion of the declutching operation and being released upon completion of the clutching operation, so that the brake means retains control until the clutching operation has been completed and until and'after completion of the declutching operation. Further, .whenthe shaft I4 is'not being driven and is at standstill, as when the clutch is engaged and flywheel 3I is not being driven, the shaft I4 may be clutched to. and declutched 'from'the flywheel 3| by axial shifting of brake member 80 in proper direction,

which is desirable to facilitate slight manual member 52, though not under the high clutching pressure available-when shaft I4 is being driven from flywheel 3I by the thrust then exerted by the strut members 60, as above explaind. It is possible, however to clutch and declutch the driving member' or' flywheel 3| to the'driven member or shaft I4 when this shaft 'is at standstill, which 'isadvantageous for the reasons stated. 7

While I preferably provide the cam balls and. cam runways therefor for effecting axial shift ing of thebrake member Wand of ther-ing 63',

as reducing friction, the invention is not limited to this form of brakeshi fting 'means. Hydraulic means, pneumatic means and "other forms 0f actuating means may be employed for effecting the axial shifting of brake member 80 ,in'the desired direction and to the desired extent for cooperation with brake member 6! in'the manner above described. The clutch member 53 may be slidably mounted on hub 40 and on flange 4301? this hub, by means of thering and collar 55, or, if desired, the clutch member 53 may have a floating mounting as provided by the selfenergizing mechanism comprising the s truts and 6|. Preferably'I provide three struts60 and three struts 6|, though the number of struts em ployed maybe varied within limits, but the minimum numberof struts ofeach kind should be three, as will be understood. p v r As previously stated, any suitable means may be provided for operating the brake lever-in proper direction to cause shifting of brake member 80 in the desired direction axiallyf I preferably provide, however, the control means shown herein and which will now be described. Shaft 133 is ,rockably mounted in ball bearings I35' suitably supported by bracket I30. 'An arm' I36 is clamped on the inner end of shaft I33 and extends downward therefrom this arm being pro- 'vided, at its lower portion, with an integral socket element I31 and, below socket element I31, with an integral eye I38 disposed substantially perpendicularto socket element I31. An upper spring abutment head I39 is pivoted to eye.l38 by meansof a'pivot bolt I40 secured thereto by means of a nut and associated washer, and a lower spring abutment head MI; is pivoted, by 'means of a bolt I42, to a boss I43 formed integrally with the web elements I44 and I45 of bracket I30, defining with adjacent portions thereof a housing for arm I36 an'd'the parts 11 associated therewith. Bolt I42 is provided, at its inner end portion, with a reduced stud I46 on which is pivoted another spring abutment head I41. A relatively heavy compression spring I48 seats at its ends against heads I39 and MI about short studs or necks extending therefrom, in a well known practice. A relatively light compression spring I50 has its lower end bearing against spring mounting head I41 and has its upper end bearing against another spring moun ing head II. The latter head is pivoted on a stud I52 secured in the lower end of an arm I53, the upper end of which is fixed on a pin I54 rockably mounted. in a bushing I55 extending through arm I36 above and at right angles to socket element I31. A two arm. pawl I51 is fixedly secured by a set screw I58 on pin I54 at the outer face of arm I36- Pawl I51 is disposed in the vertical. plane of two arms I59 and. I60 loosely mounted on a bushing I6I extending about reduced inner end portion I62 of shaft I33, the latter, being of. reduced diameter at the portion thereof passing through the inner race of the ball bearing I35, and there being a retaining ring I63 disposed about. shaft I33, between bushing IBI and the adjacent bearing I35. A snap retainer ring I64, seated in a corresponding groove in yoke I28, in which the outer bearing I35 is disposed, contacts the outer race of this latter: bearing and restrains it against endwise movement. Arm I3I contacts the inner race of the outer bearing I35, and, in cooperation with shoulder I66 of shaft I33, restrains this shaft against endwise movement. Ring I63 and shoulder I61 of shaft I33 cooperate with the inner bearing I35 to restrain these parts against relative axial movement, the arms I59 and I60 being confined between ring I63 and arm I36 and. restrained thereby against relative movement axially of shaft I33. Arm I60 extends in a direction forwardly of the press frame f, or to the right as viewed in Figure 9, and arm I59 extends rearwardly, or to the left, as viewed in Figure 9. The forward end of arm I60 is pivoted at I to the upper end of a link I1I vertically movable I through an opening I12 in web I44 of bracket I30. Arm I59 is pivoted, at its rearward end, at I13, to a link I14, this link being vertically movable through an opening I in top web I16 of bracket I30. lower end, at I18, to. the rearward end of. a transverse link I19 pivoted at its iorwardend, at I80, to link I1I. The arms I59 and I60 and the links HI and I14 and I19 together constitute a linkage system substantially in the form of a parallelogram. A link I02 is pivoted at its upper end, at I83, to link I19 adjacent link HI, and depends from link I19 in position adjacent and parallel with link HI, and extends with the latter through opening I12. Link I1I is provided, at its lower portion and in its rearward edge, with two semi-circular recesses I85 and I85a, and link I82 is provided, in its forward edge, with two semi-circular recesses I86 and I86a. In the position of the parts shown in Figure 9, recesses I65a and I86a are in register and aligned with a plunger I81. slidable. in a. bore I88 in a boss I89 I of bracket I30; Plunger I81 is provided with a stem I90; extending outward therefrom through a reduced bore I9.I. opening into bore I88. The outer portion of stem I90 is bent at right angles to provide a handle and. stop element I62 for engagement in either one of two notches I93 and I94 in the outer end of boss I89.. A compression coil spring I95 is disposed. about. stem I60, within Link I14: is: pivoted adjacent its here I60, and confined between plunger I81: and the outer end wall of bore I68. In the position of the plunger shown in Figure 10, handle I92 is engaged in notch I93, which is of less depth than notch I94, thereby holding plunger I61 in its retracted position. By pulling the plunger outward slightly, so as to disengage handle I92 from notch I63, and. turning it so as to position handle I62 in notch I 94, the plunger I81 is projected, upon release of handle I 92, so as to en age through the opening defined either-by the: lower cooperating recesses" I85a, I'86a or by the upper cooperating recesses I85; I66, depending upon Whether the links I'IIt, L82 are in their upper positions (Figure 9) or intheir lower positions. These locking functions will be later described. The links Ill and I82 are adapted to be pulled downwardly by actuating means which is typical ly illustrated by a foot treadle, although other actuating means may be employed if desired. This foot treadle is connected to the lower end of an operating rod I91 which has a laterally bent upper end I91. adapted for alternative pivotal connection either in a hole I98 in the lower end of link I1I, or in a hole I96a in. the lower end of link I02; When the operating rod I91 is coupled to hole I98- of link IN the control mechanism is thereby rendered operative to cause. a single stroke or one-cycle operation of the press when the foot treadle is depressed. When the operating rod: I01 is coupled to hole I98a of link I32 the control mechanism is thereby rendered operative to cause continuous repeating operation of. the press when the. foot treadle is depressed. Referring now to the locking functions of the recesses I85:.-I05' and I85a't86a, when the locking plunger I81 is projected through the recesses I85a and ISIia', with both links HI and I62 in their raised clutch. releasing positions, the clutch is thereby locked out so that the press cannot have any type of operation. Conversely, when the locking plunger I81 is. projected through the other recesses I85, I35, with both links HI and I82 in their lower clutch engaging positions, the clutch is held in engagement so that the crank shaft Hi can be manually rotated; or inched around for die setting purposes.

Link I'14'is pivoted at its upper end to a power actuated trip rod I99 which in turn is pivoted at its" upper end (Figure l). at 2.00 to av trip. lever 201 pivoted at. a point intermediate its ends on a stud 202 secured in. a boss 203 secured to the front of the press frame j. A counterweight 205' is suitably mounted on trip lever" 2'0I forwardly of pivot stud 202,. and urges the rearward arm 206 thereof upward into the path of a trip roll'er 201' mounted on a pivot. bolt adapted to be screwed into any one, selectively, of a series of tapped bores 208 in the hub 209' of a brake drum 2I0 keyed on crank shaft II of the press;

It will be clear from Figure 9 that arm I36 and compression spring I4 0 together constitute a toggle, and that the compression spring I48 is an over-center spring. The pressure of this overcenter spring is dominant over the pressure of the toggle strut springs GI and is capable of disengaging the clutch in opposition to the action of said latter springs. In Figure 9 the parts are shown in the positions which they occupy when arm 206 of trip lever 20I is in its depressed position shown. in Figure 1. At that time one armof pawl I51 is disposed in contact with and beneath a shoulder Ia of arm I60; Arm I36 is then held by compression spring I43 in its position shown in Figure 9, and shaft I 33 has been turned into such position that aim I3I'is members of the clutch'are declutched. In the brake setting and declutching operation the shaft I I overrunsto a certain extent, as does the crank shaft I I of the press, the overrun of the latter shaft being sufficient to move the trip roller 201 clear of trip lever 206. When it is desired to again operate the press, the treadle is depressed, moving linkI1I of Figure 9 downward. That swings arm I60 downward about shaft I33 and, since shoulder I60a of arm I60 is in contact with one arm of pawl I51 (this pawl annalso riding on the peripheries of the hub portions of the-arms I60 and I59) arm I36 is swung toward the left, as viewed in Figure 9, turning the shaft-I33 in clockwise direction. When thepivot bolt I48 is in dead center position relative to pivot stud M2 and shaft I33, thearm I3I is in the positio'nindicated by the line .r-xof Figure 1. -When' bolt I40 passes beyond dead center position, the compression spring I 48 expands, turning shaft 133 a further distance in clockwise direction and moving arm I3I tothe-position"indicated bythe line yy of Figure-1. The brake leve'r'is then in its clutch engaging and brake releasing position,-thus setting thegclutch and releasing the brake. During swinging movement of arm I36 from its position shown in Figure 9' to its oppositeposition, the secondary compression spring I50 imparts turning movement to pawl I51 in clockwise direction, through arm I53 and pin I 54, spring I50 also'being an over-center spring similarly to spring I48. -As a result of this turning movement of pawl I51, combined with the swinging movement of arm I36, when this latter arm reaches its opposite position to that shown in Figure 9, the other arm of pawl I51 is disposed beneath a shoulder I 58a of arm I59 and in contact with the peripheral hub portion of this arm and of arm I60, as before; It will be apparentthat when arm I36 has been moved into its opposite position to that shown in Figure 9,

arm I is in raised position, with pawl I51'engagedbeneathshoulder I59a, and arm I60 is in its lowered position, with pawl I51 out of contact with shoulder I60a thereof. In that position of the parts, link "I is in its lowered position, and recess I85 thereof isin register with recess I 86. of link I82, both of these links being lowered into such position that the opening defined by the recesses I85 and I86 is aligned with plunger I81; If continuous operation of the, press is desired at this time, the handle I92 of plunger I81 is disengaged from notch I93 and placed in notch I94, permitting the plunger I 81 to be projected through the'recesses I85 and 186, thus locking the links HI and I82 against upward movement andlocking shaft I33 against turning movement so that arm I3I is held in its brake releasing and clutch setting position. The trip roller 201 may also be removed from the brake drum 2I0. If, on the other hand, cyclical operation of the press is desired,the plunger I81 remains in its retracted position. treadle is depressed, causing'movement of-arm I36 into its clutch engaging and brake releasing position, after which the treadle maybe released. The cam shaft II then turns through a complete revolution, at the end of which trip roller 201 contacts arm .206 of trip lever 20 I-, forcing arm 206 downward and returning arm I36 to its-position shown in Figu're 9."-'The links I" Under such conditions, the

I ing adjustments, changing die blocks, or" in any other case where it is desirable to guardagainst unwantedoperation of the press: a

Movement of brake lever II6 in the brake engaging direction of movement is not limited but continues during the follow-up'motion of the controllable brake member 80. Movement "of said lever in the opposite direction may be limited by the associated means for shifting brake member 80 after the brake has been released, as will be readily understood. The over-center spring I48 assures full'throw of said brake lever in either direction and retains it ineither-its brake releasing and clutch applying position or in its brake setting and clutch rele'asing position, while also providing yielding operating means accommodating and compensating for wear of parts in a manner to assure proper and reliable operation of the brake-clutch mechanism. The

control means, comprising the toggle and spring arrangement shown and described, is well suited for use with the brake-clutch mechanism of my invention but, in its broader aspects, may be used to advantage with other brake or clutch mechanisms controlled by a lever having limited throw in opposite directions, or to analogous mechanisms.

l The socket element I31'ofarm I36 is intended for the reception of a suitable rod or handle 2I5, indicated in' dot and dash lines in Figure 9, insertible through either one of two openings 2I6 in bracket I 30, 'By means of handle 2 I 5, arm I 36 may be quickly swung into either of its two positions for manuallyengaging the clutch or releasing thev clutch. Sufficient leverage can be exerted through this manual handle to release the clutch even though the clutch surfaces have become tightly wedged together by'the self-en- 201 and thenoperating the clutch in each direccrank. shaft I I.

tion by the manual handle 2 I 5.

' Preferably, I provide a drag brake for retarding any objectionable overrunning of the press To that end, a flexible brake band 220, provided with asuitable brake lining 22I, is passed about brake drum 2I0, one end of this band 220 being anchored, at 222,'to a short arm 223 integralwith' a, bell-crank'brake lever 224.pivoted at its'upper end on stud 202. The other end of brake band 220 is attached to a link 225 passing through a flared opening 226 in lever224', the outer or forward endportion of this link being'threaded for reception of adjust ing nuts 221 and 228 screwing thereon, nut 228 having a rounded bearing surface contacting lever 220. At its lower end lever 224 is provided witha' boss 229 through which is threaded an adjusting screw 230 on which is threaded a jam nut 23I. Th'e rearwardend of screw 230 bears against alug 232 of thepress frame 7. It will be apparent-that 'thisscrew 230' is a pressure If desired,

screw effective for adjusting thetension of brake band 220, and that the brake band and its lining 22I cooperate with brake drum 2H) for exerting a braking eiiect upon crank shaft H so as to prevent objectionable overrun thereof while not objectionably interfering with rotation of the crank shaft in the normal operation of the press.

As above indicated, it will be understood that changes in construction and arrangement of parts of my invention may be resorted to without departing from the field and scope thereof, and I intend to include all such variations, as fall within the scope of the appended claims in this application,v in which the preferred form only of my invention has been disclosed. As illustrative of one such modification or alternative construction, the above described operating relation might be reversed so that the spring I48 would be released by manual tripping transmitted from the foot treadle and would be compressed by power tripping transmitted from the tripping roller 201.. The same mechanism can be used by reversing the attachment of the parts, as to the links HI and I'M, making suitable provision for an increase of throw of the mechanism actuated by'the tripping roller 261, and also reversing the relative throw of the double-acting ball cam mechanism 91, N30, I58, Ill-I I5,

I claim:

1. In clutch mechanism, the combination of a driving member, a rotatable driven member, a self-energizing axially shiftable clutch springbiased to engage by shifting movement in one direction, and control apparatus for said clutch comprising a servo action axially shiftable brake spring-biased to engage by shifting movement in the other direction, the spring biasing force of said brake being operative to overcome the spring biasing force of said clutch.

2. In clutch mechanism, the combination of a drivingmember, a rotatable driven member, a self-energizing axially shiftable clutch, spring means operative to axially shift said clutch into engagement in one direction, control apparatus for said clutch comprising a servo action axially shiftable brake, and spring means operative to axially shift said brake into engagement in a direction opposite to the direction of engagement of said clutch, said last named spring means being dominant over said first named spring means. l.

3. In a clutch, a driving member, a rotatable driven member, braking means for applying a braking force to said driven member comprising a non-rotatable brake member axially shiftable into brake setting position and brake releasing position, and means whereby releasing and setting of said braking means clutches and declutches said drive member to and from said driven member when the latter is at standstill.

4, In a clutch, a driving member, a rotatable driven member, braking means for stopping and holding said driven member against rotation comprising an axially shiftable rotatable brake member and a cooperating non-rotatable brake member axially shiftable into brakev setting position and brake releasing, position relative to said rotatable brake. member, means whereby said rotatable brake member is shifted axially in one direction responsive to release of said braking means and in the opposite direction responsive to setting of said braking means, and selfenergizing clutch means whereby said drive member is clutched to and declutched from said driven member responsive to axial shifting of 16' said rotatable brake member. in said one direction and in said opposite direction.

5. In a clutch, a driving member, a rotatable driven member, braking means therefor comprising a rotatable axially shiftable brake member and a cooperating non-rotatable brake member axially shiftable into brake setting position and brake releasing position relative tosaidrotatable brake member, means whereby said rotatable brake member is shifted axially in one direction responsive to release of said braking means and in the, opposite direction responsive to setting of said braking means, sup plementary means comprising self-energizing mechanism whereby said drive member is clutched to and declutched from saididriven member responsive to axial shifting of said rotatable brake member in said one direction and in said opposite direction, and means for enabling said braking means to impose braking retardation on said driven member through said self-energizing mechanism.

6. In a clutch, a driving member, a rotatable driven member, braking means therefor comprising a non-rotatable brake member axially shiftable into braking position and brake releasing position,and means actuatedby axial movement of said brake member whereby releasing and setting of said braking means clutches and declutches said drive member to and from said driven member, and also releases and applies braking force to and from said driven member,

7. In a clutch, a driving member, a. rotatable driven member, braking means for holding said driven member against rotation comprising a non-rotatable brake member axially shiftable in one direction into braking position and in the opposite direction into releasing position, and means actuated by axial movement of said brake mem ber whereby releasing and setting of said braking means clutches and declutches said drive member to and from said driven member.

8. In a clutch, a driving member, a rotatable driven member, braking means for applying braking force to said driven member comprising a non-rotatable brake member axially shiftable in one direction into braking position and in the opposite direction into releasing position, and means whereby releasing and setting of said braking means clutches and declutches said drive member to and from said driven member, said last means comprising a clutch member movable axially in the same direction with the shifting movement of said brake member.

9. In a clutch, a driving member, a rotatable driven member, braking means for holding said driven member against rotation comprising a non-rotatable braking member axially shiftable in one direction into braking position and in the opposite direction into releasing position, means actuated by axial movement of said brake member whereby release and setting of said braking means initiates clutching and declutching of said drive member to and from said driven member, and biasing spring means operative to cause the clutching and declutching operations initiated by said brake member to be completed.

10. In a clutch, a driving member, a rotatable driven member, braking means for stopping said driven member and holding it against rotation, said braking means comprising a non-rotatable braking member axially shiftable in one direction into braking position and in the opposite direction into releasing position, means actuated'by axial movement of said brake member whereby release andsetting or said braking means initiates clutching, and declutching of said drive member to and from said driven member, andsupplementary means whereby the clutching and declutch- :ingoperations initiated by said brake member are completed, said braking means being released only upon completion of the clutching operation and said declutching operation being completed .only' upon setting of said braking means.

7 11. ,In a clutch, a driving member, a rotatable driven member, braking means for holding said driven member against rotation comprising a non-rotatablebrake member axially shiftable in one direction into braking position and in'the f opposite direction into releasing position, means actuated-by axial movement oi said brake memberpwhereby release and setting of said braking meansinitiates clutching and declutching of said driyemember to and fromsaid driven member, and supplementary, means comprising servo mechanism receiving rotative' energy from said rotatable driven member and arranged whereby the declutching operations initiated by said brake member are assisted by servo energy.

12. In combination, a rotatable driving member, a rotatable driven mem ber, a clutch for coupling said members together, self-energizing mechanism for actuating said clutch, and brake means for controlling said self-energizing mechanism comprising an axially shiftable rotatable brake member and a co-acting axially shiftable non-rotatable brake member, said brake means being-operative to apply braking retardation to said rotatable driven member through said axially shiftable non-rotatable brake member when said clutch is released. 1-3; In' combination, a'rotatable driving memher, a rotatable driven member, a clutch therebetween, self-energizing mechanism for actuating' said clutch, said self-energizing mechanism comprising two cooperating relatively rotatable self-energizing members adapted to have relative axial movement occurtherebetween. when one of; said self-energizing members is rotated relatively tothe other, means for driving one of said self-energizing members from said rotary driven member, braking means for retarding rotation of the other self-energizing member to cause'relative axial movement between said selfenergizing, members, said braking means comprising'an axially shiftable rotatablebrake member andv a co-acting manually controlled axially shiftable non-rotatable brake member, means for transmitting said relative axial movement to said clutch for controlling the latter, and means enabling said braking means to stop said driven member and to hold it against rotationaiter release of said clutch.

' axial movement to said first brak member durclutching position in the brakereleasing operation, and self-energizing mechanism whereby said clutch member is movedinto clutching position and declutching position responsive to set- .tingand releasing of said braking means.

15. Ina clutch, a rotatable shaft, a driving clutch member, a hub fixed on said shaft, a driven clutch membermounted on said hub for relative axial and turning movement, self-energizing means connecting said driven clutch member and said hub comprising drive transmittingstruts, an abutment member fixed on said hub, a brake membenmounted on said hub-for relative axial and turning movement betweensaid abutment member andsaid drivenclutch member in end- .wise abutment withthe latter, and a non-rotatabie brakemember axially shiftable into brakesetting position and brake releasing position relative to. said first brake member, said second brake member moving said first brake member axially andfthereby moving said driven clutch member axially into declutching position during the brake setting operation, andsaid self-energizing means moving said driven clutch member axially into clutching position and thereby imparting similar ing the-brake releasing operation. I V 7 .16. In a clutch, a rotatable'shaft, a driving clutch member, ahub fixed on said shaft,.a drivenclutch member mounted on said hub for relative axial and turning. movement self -energizing means connectingsaid driven clutch memher and said hub comprising drive transmitting struts; and oppositely related yielding energy storing struts, an abutment member fixed on. said hub, a brake member mounted on said hub 'for' relative axial and turning movement betweensaidabutment member and said driven. clutch member in endwise abutment with the latter, said I brake member'andsaid abutment member having cooperating cam ,meanswhereby} said brake member -ismoved axially in .a direction; toward and-in a direction away irom said driven clutch member responsive to turning of said brake member in. one direction and in the opposite direction, and anon-rotatablebrxke member axially shiftable into brake setting position and brake releasing position relative to said first brake memher, said second brakemember moving said first -14. In a clutch. a driving member, a rotatable driven member, braking means for stopping said driven member and holding it against rotation, said braking means comprising an axially shiftable rotatable brake member and a cooperating non-rotatable brake member axially shiftable into brake setting position and brakereleasing position relative to said rotatable brakemember, the latter member being axially movable by said non-rotatable member in the movement thereof in brake setting direction, clutch means comprising a shiftable clutch member for clutching and,

declutchingsaiddriving member to and from said driven member, said clutch member shifting axially directly with and in the same direotionas 7 said rotatable brake member into declutching position in the brake setting operation and into brake member axially and in cooperation with said self-energizing means causing turning of said driven clutch member and said first brake member in said one direction thereby moving said driven clutch member axially into declutching position during the brake setting operation, said yielding struts being compressed by overrunning of, said shaft after declutching and setting of .thebraking means, said self-energizing means acting. to turnsaid driven clutch member and said first brakemember in said opposite direction andto thereby move said driven clutch into clutching position during the brake releasing operation.

17 In a clutch a rotatable shaft, a ems driving cone clutch member having an outwardly converging clutching surface,- a hub fixed on said shaft, adriven male cone clutch member mounted on said hubfor relative axial and turning movementcooperating with said female member, self-energizing meansconnecting said hub an'd said male member comprising drive transmitting struts, an abutmentmember fixedon said hub outward from said male member, amale cone brakemember mounted, on said hub for relative axialla'nd turning movement between said abutment member and said male clutch member, said brake member having an outwardly converging braking surface, a cooperating non-rotatable female brake member axially shiftable into brake setting position and brake releasing position relative to said male brake member, and means whereby setting said braking means shifts said male clutch member axially into de-clutching position, said self-energizing means moving said male clutch member axially outward into clutching position in the brake releasing operation.

18. In a clutch, a pair of driving and driven cone clutch members, one of said members being axially shiftable relative to the other into declutching position and clutching position, a pair of axially shiftable cooperating cone brake members operative to apply braking force to said driven clutch member, one of said brake members being axially shiftable relative to the other into brake setting position and brake releasing position, and means whereby setting and releasing of said braking means shifts said one clutch member axially into declutching position and into clutching position.

19. In a clutch, a female cone clutch member having an outwardly converging clutching surface, a cooperating male cone clutch member axially shiftable into clutching position and declutching position, an axially shiftabiemale cone brake member disposed outward of said male clutch member and having an outwardly converging clutching surface, a cooperating female cone brake member axially shiftable into brake setting position and brake releasing position relative to said male brake member, and means whereby setting and release of said braking means shifts said male clutch member axially into declutching position and clutching position, said latter means enabling said brake members to hold said male clutch member against rotation when said clutch is disengaged.

20.. In a clutch, a femal cone clutch member, a cooperating male cone clutch member axially shiftable into clutching position and declutching position, an axially shiftable male cone brake member, a cooperating female cone brake member axially shiftable into brake setting position and brake releasing position relative to said male brake member, the clutching surfaces of said clutch members and the braking surfaces of said brake members being similarly inclined, and means whereby setting and release of said braking means shifts said male clutch member axially into declutching position and clutching position, and applies braking retardation to said male clutch member when in declutching position.

21. In a clutch, a pair of cooperating driving and driven cone clutch members, a pair of cooperating cone brake members one axially shiftable relative to the other into brake setting position and brake releasing position relative thereto and said other brake member being axially shiftable with said one brake member in continued movement of the latter in brake setting direction and in brake releasing direction, and means whereby setting and release of said braking means shifts one of said clutch members into declutching position and clutching position, and also applies braking force to the driven clutch member for holding it against rotation in said declutching position.

22. In a clutch, a pair of cooperating driving and driven cone clutch members, a pair of cooperating cone brake members, one of said brake members being non-rotatable and axially shiftable relative to the other brake member into brak setting position and brake releasing position relative thereto and said other brake member being axially shiftable with said one brake memher in continued movement of the latter in brake setting direction and in brake releasing direction, and means whereby setting and release of said braking means shifts one of said clutch members into declutching position and clutching position, and applies braking force to the driven clutch member in said declutching position.

23 In a clutch, a female cone clutch member, a cooperating male cone clutch member axially shiftable into clutching position and declutching position, an axially shiftable male cone brake member disposed in endwise abutting relation to said male clutch member, a cooperating female cone brake member axially shiftable into brake setting position and brake releasing position relative to said male brake member, the latter being axially shiftable with said female brake member in continued movement thereof in brake setting direction and brake releasing direction, continued movement of said female brake memberin brake setting direction shifting said male cone clutch member axially into declutching position and applying braking retardation to said male clutch member for stopping rotation thereof, and supplementary means whereby release of said braking means shifts said male clutch member axially into clutching position.

24. Incombination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a shift lever with limited movement in opposite directions into two operative positions, manual means for moving said lever in one direction a distance less than its full throw, power means responsivetothe engagement of said clutch means for moving said lever in the opposite direction a distance less than its full throw, and yielding means for completing the throw of said lever in either direction.

25. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a shift lever with. limited movement in opposite directions into two operative positions, a rockably mounted arm connected to said lever, toggle means connected to said arm, and mechanism for turning said arm in 7 either direction beyond dead center position of said toggle means comprising power driven means responsive to said clutch means for effecting the turningin one direction, said toggle means comprising an over center spring effective for completing the throw of said arm and said lever in either direction.

26-. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a shift lever with limited movement in opposite directions into two operative positions, a rockably mounted shaft, an operating arm secured on saidshaft having operating connection to said lever, toggle means connected to said shaft, and manual means and power means responsive to said clutch means for turning saidshaft in either direction 21 beyond dead center position of said toggle means, the latter comprising an over center spring effective for completing the throw of said arm and said lever in either direction.

27. In clutch mechanism for punch presses and the like, the combination of a driven shaft, a clutch controlling th rotation of said shaft, brake means governing said clutch comprising a non-' rotatable axially shiftable brake member, a foot treadle for shifting said brake member in one direction for initiating the engagement of said clutch, power means actuated by said driven shaft for shifting said brake member in the opposite direction for effecting the disengagement of said clutch, and automatic control mechanism responsive to said foot treadle and to said power means for controlling the shifting of said brake member, said control mechanism comprising a first actuating member towhich said foot treadle is adapted to be connected for producing single stroke operation of the punch'press, and a second actuating member to which said foot treadle is adapted to be connected for producing repeating operation of the punch press.

28. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a rockably mounted shaft, toggle means comprising an operating arm secured at one end on said shaft and an over center compression spring connected to the other end of said arm, linkage and pawl means for turning said shaft in either direction beyond dead center position of said toggle means, said spring completing throw of said shaft in either direction, manual means for actuating said linkage and pawl means in one direction, and power means responsive to said clutch means for actuating said linkage and paw] means in the other direction.

29. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a operating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a rockably mounted shaft, togglemeans comprising an operating arm secured at one end on said shaft and an over center compression spring connected to the other end of said arm, means comprising a linkage parallelogram distortable from a first position to a second position for turning said shaft in either direction beyond dead center position of said toggle means, manual means for actuating said parallelogram in one direction, power means responsive to said clutch means for actuating said parallelogram in the opposite direction, and means for locking said linkage parallelogram against distortion in either of its said positions.

30. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a rockably mounted shaft, two arms loosely mounted about said shaft projecting oppositely therefrom, an end link substantially parallel with said arms, two side links connecting the outer ends of said arms to said end link forming therewith a parallelogram, manual means for imparting endwise movement to one of said side links, power means responsive to the engagement of said clutch means for imparting endwise movement to the other of said side links, and means cooperating with said arms and with said shaft for rocking the latter in opposite directions responsive to endwise movement of said side links.

31. In combination, clutch means, brake means governing said clutch means comprising a rotatable axially shiftable brake member and a cooperating non-rotatable axially shiftable brake member, control mechanism for controlling said latter brake member comprising a rockably mounted shaft, two arms loosely mounted about said shaft projecting oppositely therefrom, an end link substantially parallel with said arms, two side links. connecting the outer ends of said arms to said end link forming therewith a parallelogram, power means responsive to said clutch means and manual means for imparting endwise movement to either of said side links, means cooperating with said arms and with said shaft for rocking the latter in opposite directions responsive to endwise movement of said side links, and means for locking said parallelogram against movement in either position of said shaft.

' 32. In combination, clutch means, brake means governing said clutch means comprising a nonrotatable axially shiftable brake member, control mechanism for controlling said brake member comprising a rockably mounted shaft, toggle means comprising an operating arm secured at one end on said shaft and an over center compression' spring connected to the other end of said arm, two arms loosely mounted about said shaft projecting oppositely therefrom, an end link below said shaft substantially parallel with said arms, two side links connecting the outer ends of said loosely mounted arms and said end link forming therewith a parallelogram, a pawl pivoted on said operating arm, said pawl and said loosely mounted arms having cooperating elements for turning said shaft beyond dead center position of said toggle means in one direction when one of said side links is moved downward and in the other direction when the other side link is moved downward, an over center compression spring for positioning said pawl in cooperating relation to the respective loosely mounted arms responsive to movement of said operating arm from one position to the other, manual means for actuating one of said side links, and power means responsive to the engagement of said clutch means for actuating the other of said side links. a

33. In combination, clutch means, brake means governing said clutch means comprising a nonrotatable axially shiftable brake member, control mechanism for controlling said brake member comprising a shift lever with limited movement in opposite directions into two operative positions, an operating shaft connected to said lever, an arm secured to said shaft, an over center spring connected to said arm effective for completing throw thereof in either direction, means for turning said arm in one direction beyond dead center position of said spring, and power driven means responsive to the engagement of said clutch means for turning said arm in the other direction beyond dead center position of said spring, said arm having a socket element disposed substantially transversely of said shaft manually in either direction.

CLARENCE M. EASON. 

